Injection pump control arrangement



Sept. 1, 195 9 K. SCHLICHTENMAYER INJECTION PUMP CONTROL ARRANGEMENT F iled Aug. 9, 195'? INVENTOR 12w i United States Patent Ofiice 2,902,018 Patented Sept. 1, 1959 INJECTION PUMP CONTROL ARRANGEMENT Karl Schlichtenmayer, Stuttgart-Wangen, Germany, assignor to Robert Bosch G.m.b.H., Stuttgart, Germany Application August 9, 1957, Serial No. 677,358

Claims priority, application Germany August 14, 1956 12 Claims. (Cl. 123-140) The present invention relates to internal combustion engines.

More particularly, the present invention relates to that type of internal combustion engine wherein the fuel is supplied by an injection pump, and the present invention relates to the controls for such an injection pump.

Experience has shown that in internal combustion engines of the above type the influence of an automatic control responsive to changes in the speed of operation of the engine on a member which controls the amount of fuel supplied by the injection pump should diminish as the valve in the intake manifold is opened to an increasing degree and at full-load the control which is responsive to the speed of the engine should have no influence on the amount of fuel supplied by the injection pump. When these latter conditions are obtained, the most favorable fuel-air ratio is provided. The amount of fuel supplied by the injection pump at a full-load position of the supply control element of the injection pump with the valve of the intake manifold in its fully opened position is regulated throughout the entire range of speed of the engine at full-load with respect to the amount of air drawn into the engine at full-load in any known way, as, for example, by a compensating valve.

One of the objects of the present invention is to provide a structure which will fulfill the above requirements, which is to say a structure which when the engine is at no-load or idling will provide a maximum range of movement of the supply control member of the injection pump in response to changes in the speed of operation of the engine, which will provide a gradually diminishing influence of changes in the engine speed on the supply control member as the load increases, and which will eliminate influence of engine speed changes on the supply control member of the injection pump at full-load.

Another object of the present invention is to provide a relatively simple structure which will effectively accomplish the previous object and which will provide proper cooperation between regulation of the injection pump by the operator and automatic regulation of the injection pump by the speed of the engine itself.

A further object of the present invention is to provide an arrangement capable of controlling an injection pump supply not only in the manner referred to above but in addition in accordance with changes in one or more variables such as variations in the outer atmospheric temperature and pressure.

An additional object of the present invention is to provide a structure of the above type which is capable of being operated so that the fuel supply can be terminated at any moment at the will of the operator independently of structures which automatically control the fuel supply.

With the above objects in view, the present invention combines an operator-controlled moving means and an engine-controlled moving means both of which are connected to a supply control means of an injection pump in such a way that the supply control means of the injection pump can be moved by either of these moving means with the engine-controlled moving means functioning so as to be capable of moving the fuel supply control means through a maximum range for a given range of movement of the engine-controlled moving means when no-load conditions are present, this enginecontrolled moving means moving the fuel supply control means through a gradually diminishing range for the predetermined range of movement of the engine-controlled moving means as the operator moves the operator-controlled moving means from its no-load towards its full-load condition, and the engine-controlled moving means being incapable of moving the fuel supply control means in response to changes of engine speed when the operator-controlled moving means is at its full-load position.

The novel features which are considered as characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construction and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings, in which:

Fig. 1 is a schematic illustration of one possible structure according to the present invention;

Fig. 2 is a fragmentary schematic illustration of structure of Fig, 1 combined with structure for controlling the fuel supply in accordance with variables in addition to those present in the structure of Fig. l; and

Fig. 3 is a fragmentary sectional view taken along line III-Ill of Fig. 2 in the direction of the arrows.

Referring to Fig. 1, a shaft 1 is illustrated in the lower portion of Fig. l and this shaft is supported for rotation about its axis and is driven by the unillustrated internal combustion engine at a speed of rotation at all times which is proportional to the speed of the engine. This shaft 1 carries the schematically illustrated centrifugal governor shown in the lower portion of Fig. l as provided with the fiyweights 2. A sleeve 3 schematically shown in Fig. 1 is axially shiftable along the shaft 1 and is urged by the spring 4 to a rest position shown in solid lines in Fig. 1, the centrifugal governor also being illustrated in solid lines in its rest position. During idling of the engine the parts 2 and 3 remain in the solid line position of Fig. l, and as the speed of the engine increases the flyweights 2 move out away from the axis of the shaft 1 and at the maximum speed of the engine the centrifugal governor has the dotted line position shown in Fig. 1, and this governor is operatively connected with the sleeve 3 to shift the latter to the right through the distance a against the force of the spring 4 when the engine is operating at its maximum speed.

The sleeve 3 is formed with an annular groove or the like into which the bottom free end portion of a lever 5 extends so that this lever 5 can turn about an axis passing through its bottom end portion, as viewed in Fig. 1, and at the same time the bottom end portion of the lever 5 is axially shiftable together with the sleeve 3. The lever 5 is formed distant from the sleeve 3 with an elongated arcuate slot 6 into which a pivot pin 7 extends, this pivot pin 7 forming a pivot axis means for the lever 5 and being shiftable along the slot 6 so as to change the pivot axis of the lever 5, the lever 5 being turnable about the pivot axis provided by the pivot pin 7 in response to axial movement of the sleeve 3.

As is shown in Fig. 3 as well as Fig. 1, the pivot pin 7 is fixed to an end of a bell crank 8, and as is apparent from Fig. 1 this bell crank 8 is pivotally supported at 9 for turning movement about a stationary axis. The end of the bell crank 8 distant from the pivot pin 7 is pivotally connected with one end of a rod 10 whose opposite end is pivotally connected with a free end of a lever 11 connected to a butterfly valve 14 in the intake manifold 15, as shown schematically in Fig. 1, so that turning of the lever 11 turns the valve 14. A further rod 12 is pivotally connected at the junction of lever 11 and rod 10 and the opposite end of the rod 12 is pivotally connected with a lever 13 turnable at its bottom end about a stationary axis and being accessible to the operator so that when the operator engages a pedal, for example, connected to the lever 13 the latter may be turned.

As is shown in Fig. 3, the free end portion of the lever 5 which is distant from the sleeve 3 is of U-shaped cross-section and terminates in a relatively short portion located opposite the top end of the slot 6 and formed with an opening which receives the pivot pin 17, the latter being coaxial with the pivot pin 7 when this latter pivot pin is moved by the operator through the operatorcontrolled moving means 813 to a full-load position. This pivot pin 17 is fixed to a link 18 whose end distant from the pivot pin 17 is pivotally connected with an injection pump fuel supply control member 19, in the embodiment of Fig. 1, this member 19 being carried for linear shifting movement by a suitable support means and the member 19 cooperating in a known way with an unillustrated injection pump for varying the amount of fuel delivered by the pump to the engine. As is indicated by the legend stop and the arrow thereover in Fig. 1, the fuel supply diminishes as the control member 19 moves to the left and increases when the member 19 shifts in the opposite direction.

The parts are illustrated in Fig. 1 in solid lines in the position which they take at full-load. In this position to which the operator has turned the lever 13, the structure has moved the valve 14- to its full open position, and the bell crank 8 has been turned so as to locate the pivot pin 7 in a position where its axis coincides with the axis of the pivot pin 17. As is shown by a comparison of the solid and dotted line positions of the lever 5 in Fig. 1, over the entire range of movement a of the sleeve 3 the lever 5 will be turned about the pivot pin 7 without having any influence at all on the fuel supply control member 19 when the operator-controlled moving means 813 has located the pivot pin 7 in its full-load position.

The idling position of the parts is illustrated in Fig. 1 in dot-dash lines. In this position the valve 14 has been moved by the illustrated linkage so close to its fully closed position that the amount of air taken in through the intake manifold 15 is only sufficient to support idling of the engine. The movement of the operatorcontrolled moving means 8-43 to the dot-dash line position of Fig. 1 locates the pivot pin 7 in the position indication at 7, this being an end position of the pivot axis means of the lever 5 which is distant from the fullload position of this pivot axis means. The turn of the pivot pin 7 to the position 7 causes the fuel supply control member 19 to be shifted in the stop direction through the distance Z: of Fig. 1.

It is apparent from Fig. 1 that when the pivot pin 7 is in the end position 7' the extent of movement of the member 19 in response to shifting of the sleeve 3 through a predetermined range of movement will be at a maximum, and this extent of movement of member 19 in response to a predetermined range of movement of the sleeve 3 will gradually diminish as the pivot pin 7 approaches its full-load position, and when the pivot pin 7 is in its full-load position then movement of the sleeve 3 and the resulting turning of the lever Swill have no influence on the fuel supply control member 19.

In the embodiment of Fig. 2, the link 18 is not connected directly with the fuel supply control member 19 of the injection pump. Instead the link 18 is pivotally connected at its end distant from the pivot pin 17 with one arm of a two-arm lever 21 which is pivotally supported intermediate its ends by the pivot pin 22. The arm of lever 21 on the side of pivot pin 22 distant from link 18 pivotally supports with the pivot pin 23 which is carried by the lever 21, a second two-arm lever 24 which is engaged at one end by an end of a compression spring 25 whose opposite end presses against a projection 26 which is integral with the lever 21. The spring 25 urges the lever 24 in a counterclockwise direction about the pivot pin 23 into engagement with a stop 27 fixedly carried by the lever 21. The end of the lever 24 distant from the stop 27 is pivotally connected with one end of a link 28 whose opposite end is pivotally connected with the fuel supply control member 19.

The pivot pin 22 is supported for eccentric turning movement about an eccentric axis parallel to and spaced from a turning axis provided by the pivot pin 22 itself, and this support is provided by a shaft 30 which at one of its ends fixedly carries the pivot pin 22 spaced from the axis of the shaft 30, this shaft 30 itself being tumably supported in an opening formed in a second shaft 34, and it will be noted that the axis of the shaft 34 is spaced from and parallel to the axis of the shaft 30. A bellows or other known device 32 which is responsive to changes in atmospheric pressure and temperature is connected with a lever 31 which is in turn connected with the shaft 30 to turn the latter about its axis in response to changes in atmospheric temperature and pressure. As a result, the pivot pin 22 turns about the axisv of the shaft 30 and acts through the lever 21 and the lever 24 as well as the lever 28 on the member 19 to change the fuel supply in accordance with variations in atmospheric pressure and temperature without influencing and in a manner entirely independent of the abovedescribed operator-controlled means and engine-controlled means for regulating the position of the fuel supply control means 19.

The shaft 34 is itself supported in a suitable housing for rotation about its axis, and such turning of the shaft 34 will provide a turning of the shaft 30 together with the pin 22 about the axis of the shaft 34. A lever 35 interconnects the shaft 34 with a means responsive to variations in another variable, and in Fig. 2 there is diagrammatically illustrated a cooling water thermostat 36 which is responsive to changes of the temperatures of the cooling Water for turning the lever 35 so as to turn the shaft 34 and in this way control the position of the member 19 in response to changes in a second variable and in a manner completely independent of the other structure which controls the position of the fuel supply control member 19. All changes in the position of the pivot pin 22 result in movement of the element 19.

A means is provided for stopping the supply of the fuel at the will of the operator independently of all of the structure described above, and this means is shown in Fig. 2 as taking form of a lever 39 pivotally supported intermediate its ends by a stationary pivot pin 38 and having an upper free end which is capable of acting on a control member 19 through the link 28. The opposite end of the lever 39 is connected witha pull cable 40 which is capable of being manually pulled by the operator in a stop direction indicated in Fig. 2 for moving the member 19 in its stop direction-indicated in Fig. 2. The engagement of the lever 39 with the link 28 upon pulling of the cable 40 causes the element 19 to be shifted to the left, as viewed in Fig. 2 while the lever 24 turns in a clockwise direction against the force of the spring 25, and the fuel supply control member 19 may be shifted in this manner until it engages an unillustrated stop which determines the position of the member 19 when no more fuel is supplied by the injection pump so that at this time the fuel supply to the engine is cut off and the engine stops.

It will be understood that each of the elements dese fl fiq above, or two or more together, may also find a useful application in other types of internal combustion engines differing from the types described above.

While the invention has been illustrated and described as embodied in injection pump controls, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can by applying current knowledge readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the following claims.

What is claimed as new and desired to be secured by Letters Patent is:

1. In an internal combustion engine, in combination, movable supply control means for controlling the amount of fuel supplied by an injection pump of the internal combustion engine in accordance with the position to which said movable supply control means is moved; operator-controlled moving means operatively connected to said supply control means for moving the latter at the will of the operator between a no-load position where a minimum amount of fuel is supplied by the injection pump and a full-load position where a maximum amount of fuel is supplied by the injection pump; and enginecontrolled moving means responsive to changes in the speed of operation of the engine and also connected to said supply control means for moving the latter between said positions thereof, said engine-controlled moving means and said operator-controlled moving means cooperating with each other to provide, for a predetermined range of movement of said engine-controlled moving means due to changes in the speed of operation of the engine, a maximum amount of movement of said supply control means in response to operation of said enginecontrolled moving means when said operator-controlled moving means is in its no-load position, and an extent of movement of said supply control means in response to operation of said engine-controlled moving means which gradually diminishes as said operator-controlled moving means approaches its full-load position and which becomes zero when said operator-controlled moving means is in its full-load position, so that in the latter position of said operator-controlled moving means said enginecontrolled moving means will have no influence on said supply control means.

2. In an internal combustion engine, in combination, movable supply control means for controlling the amount of fuel supplied by an injection pump of the internal combustion engine in accordance with the position to which said movable supply control means is moved; operator-controlled moving means operatively connected to said supply control means for moving the latter at the will of the operator between a no-load position where a minimum amount of fuel is supplied by the injection pump and a full-load position where a maximum amount of fuel is supplied by the injection pump; engine-controlled moving means responsive to changes in the speed of operation of the engine and also connected to said supply control means for moving the latter between said positions thereof, said engine-controlled moving means and said operator-controlled moving means cooperating with each other to provide, for a predetermined range of movement of said engine-controlled moving mean due to changes in the speed of operation of the engine, a maximum amount of movement of said supply control means in response to operation of said engine-controlled moving means when said operator-controlled moving means is in its no-load position, and an extent of movement of said supply control means in response to operation of said engine-controlled moving means which gradually diminishes as said operator-controlled moving means approaches its full-load position and which becomes zero when said operator-controlled moving means is in its full-load position, so that in the latter position of said operator-controlled 'moving means said enginecontrolled moving means will have no influence on said supply control means; and at least one additional moving means operatively connected with said supply control means for controlling the latter independently of both of said moving means in response to changes in the operating conditions affecting combustion in the engine.

3. In an internal combustion engine, in combination, movable supply control means for controlling the amount of fuel supplied by an injection pump of the internal combustion engine in accordance with the position to which said movable supply control means is moved; operator-controlled moving means operatively connected to said supply control means for moving the latter at the will of the operator between a no-load position where a minimum amount of fuel is supplied by the injection pump and a full-load position where a maximum amount of fuel is supplied by the injection pump, said operator-controlled moving means also being connected operatively with a valve in an intake manifold of the engine for moving the valve between closed and opened positions as said operator-controlled moving means is moved between its no-load and full-load positions, respectively; and engine-controlled moving means responsive to changes in the speed of operation of the engine and also connected to said supply control means for moving the latter between said positions thereof, said engine-controlled moving means and said operator-controlled moving means cooperating with each other to provide, for a predetermined range of movement of said engine-controlled moving means due to changes in the speed of operation of the engine, a maximum amount of movement of said supply control means in response to operation of said engine-controlled moving means when said operatorcontrolled moving means is in its noload position, and an extent of movement of said supply control means in response to operation of said enginecontrolled moving means which gradually diminishes as said operator-controlled moving means approaches its full-load position and which becomes zero when said operator-controlled moving means is in its full-load position, so that in the latter position of said operator-controlled moving means said engine-controlled moving means will have no influence on said supply control means.

4. In an internal combustion engine, in combination, support means; a supply control member movably supported by said support means and adapted to vary the amount of fuel delivery by an injection pump in accordance with the position of said supply control member on said support means; an elongated lever having a first portion connected operatively with said supply control member for moving the latter in response to movement of said first portion of said lever and having a second portion distant from said first portion; engine-controlled lever moving means operatively connected with said second portion of said lever for moving said second portion of said lever through a predetermined range of movement in response to changes in the speed of operation of the engine; pivot axis means operatively connected to said lever to form a pivot axis therefor and shiftable with respect to said lever from a position coinciding with said first portion of said lever to an end position intermediate said portions of said lever so that the movement of said supply control member is zero in response to movement of said second portion of said lever when said pivot axis means is in said position coinciding with said first portion of said lever and so that the extent of movement of said supply control member in response to movement of said second portion of said lever gradually increases as said pivot axis means approaches said end position thereof; and. operator-controlled lever moving means operable at the will ofthe operatorand connected with said pivotaxis means for locatingthe latter in said'position coinciding with said first portion of said. lever when said operator-controlled means is in a full-load position, for moving said pivot axis means towards said end posi tion thereof as. said operator-controlled meansapproaches a, no-load position and for locating saidpivot axis means inits end position when said operator-controlled means is in. said no-loadposition thereof, said pivot axis means as it moves toward and away from said end position thereof turning said lever about an axis passing through said second portion of said lever for. moving said first portion of said lever and said supply control member therewith.

5. In an internal combustion. engine; in combination, support means; a supply'control member movably supported by said. support means and adapted to vary the amount of fuel delivery by an injection pump in accordance with the position of said supply control member on. said support means; an elongated lever having a first portion connected operatively with said supply control member for moving the latter in response to movement of said first portion of said lever and having a second portion distant from said first portion; engine-controlled lever; moving means operatively connected with said second portion of said lever for moving said second portion of said. lever through a predetermined range of movement in response to changes in the speed of operation of the engine; pivot axis means operatively connected to said lever to form a pivot axis therefor and shiftable with respect to saidlever from a position coinciding with said first portion of said lever to an end position intermediate said portions of said lever so that the movement of said supply control member is zero in response to movement of said "second portion of said lever when said pivot axis means is in said position coinciding with said first portion of said lever and so that the extent of movement of said supply control member in response to movement of said secondportion of said lever gradually increases as said pivot axis means approaches said end position thereof; operator-controlled lever moving'means operable at the will of the operator and connected with said pivot axis means for locating the latter in said position coinciding with said first portion of said lever when said operator-controlled means is in a full-load position, for moving said pivot axis means towards said end position thereof as said operator-controlled means approaches a no-load position and for locating said pivot axis means. in its end position when said operator-controlled means is in said no-load position thereof, said pivot axis means as it moves to- Ward and away from said end position thereof turning said lever about an axis passing through said second portion of said lever for moving said first portion of said lever and said supply control member therewith; and valve means in an intake manifold of the engine connected operatively with said operator-controlled lever moving means and movable between closed and opened positions as said operator-controlled lever moving means moves between its no-load and full-load position, respectively.

6. In an internal combustion engine as recited in claim 4, said lever being formed-With an elongated arcuate slot one end of which is located at said first portion of said lever and the other end of which determines said end position of said pivot axis means, said pivot axis means being in the form of a pin shiftable along said slot.

7. In an internal combustion engine as recited in claim 4, said engine-controlled lever moving. means including a shaft rotatable at a speed proportional to the speed of the engine, a sleeve shiftable axially along said shaft and connected operatively with said second portion of said. lever for. shifting the latter with said sleeve, and

centrifugal governor means carried by said shaft and connected operatively with said sleeve for shifting the latter as the speed of rotation of said shaft changes.

8. In an internal combustion engine as recitedin claim 4,. the operative connection between. said first portion of said lever and said supply control member being formed by a linkage which includes a second lever; a pivot pin operatively connected to said second lever in.- termediate its ends so that said second lever is pivotal about said pivot pin; eccentric support means supporting said pivot pin for turning. movement about an. eccentric axis parallel to and spaced from the turning axis provided by the pivot pin itself; moving means responsive to a predetermined variable affecting combustion inthe engine and operatively connected with said pivot pin for turning the same about said eccentric axis in response to changes of. said predetermined variable; and means for transmitting movement of said second lever to said supply control member when said pivot pin turns about said eccentric axis Without disturbing the position of. said first-mentioned lever.

9. loan internal combustion engine asrecited in claim 8, said eccentric support means being itself turna-ble about a second eccentric axis parallel to and spaced from said first-mentioned eccentric axis; and means responsive to changes of a second predetermined variable affecting' combustion in. the engine operatively connected to said eccentric support means for turning the latter about said second eccentric axis so that changes in said second variable also actuate said second lever to position.

said supply control member accordingly.

l0. Inan internal combustion engine, in combination, movable supply control means for controlling the amount of fuelsupplied by at injection pump of the internal combustion engine in accordance with the position to which said'movable supply control means is moved; operatorcontrolled moving means operatively connected to said supply control means for moving the latter at the will of the operator between a no-load position 'Where a minimum amount' of fuelis supplied by the injection pump and a full-load position where a maximum amount of fuel is supplied by the injection pump; engine-controlled moving means responsive to changes in the speed of operation of the engine and also connected to said supply control means for moving the latter between said positions thereof, said engine-controlled moving means and said operatoncontrolled moving means cooperating with each other to provide, for a predetermined range of movement of said engine-controlled moving means due to changes in the speed of operation of the engine, a maximum amount of movement of saidsupply control means in response to operation of said engine-controlled moving means when said operator-controlled moving means is in its no-load position, and an extent of movement of said supply control means in response to operation of said engine-controlled moving means which gradually diminishes as said operator-controlled moving means approaches its full-load position and which becomes zero When said operator-controlled moving means is in its full-load position, so that in the latter position of said operator-controlled moving means said enginecontrolled moving means will have no influence on said supply control means; and operator-controlled means cooperating with said supply control means for moving. the same to a position where no fuel is supplied at the will of the operator.

11. In an internal combustion engine, in combination, support means; a supply control member movably supported by said support means and adapted to vary the amount of fuel delivery by an injection pump in accordance with the position of said supply control member on said support means; an elongated lever having a first portion connected operatively with said supply control member for moving the latter in response to movement of said first portion of said lever and having a second.

portion distant from said first portion; engine-controlled lever moving means operatively connected with said second portion of said lever for moving said second portion of said lever through a predetermined range of movement in response to changes in the speed of operation of the engine; pivot axis means operatively connected to said lever to form a pivot axis therefor and shiftable with respect to said lever from a position coinciding with said first portion of said lever to an end position intermediate said portions of said lever so that the movement of said supply control member is Zero in response to movement of said second portion of said lever when said pivot axis means is in said position coinciding with said first portion of said lever and so that the extent of movement of said supply control member in response to movement of said second portion of said lever gradually increases as said pivot axis means approaches said end position thereof; operatr-controlled lever moving means operable at the will of the operator and connected with said pivot axis means for locating the latter in said position coinciding with said first portion of said lever when said operator-controlled means is in a full-load position, for moving said pivot axis means towards said end position thereof as said operator-controlled means approaches a no-load position and for 10- cating said pivot axis means in its end position when said operator-controlled means is in said no-load position thereof, said pivot axis means as it moves toward and away from said end position thereof turning said lever about an axis passing through said second portion of said lever for moving said first portion of said lever and said supply control member therewith; and operatorcontrolled moving means cooperating with said supply control member for moving the latter to a position providing no fuel supply at the will of the operator independently of all other elements which cooperate with said supply control member.

12. In an internal combustion engine as recited in claim 11, said last-mentioned operator-controlled means including a lever pivotally supported intermediate its ends having a free end cooperating with said supply control member, and a pull cable connected to the opposite end of the latter lever for turning the same to move said supply control member.

References Cited in the file of this patent UNITED STATES PATENTS 2,474,121 Sanders June 21, 1949 2,708,921 Links May 24, 1955 FOREIGN PATENTS 835,814 Germany Apr. 3, 1952 

